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Publication numberUS2558752 A
Publication typeGrant
Publication dateJul 3, 1951
Filing dateJul 9, 1948
Priority dateJul 9, 1948
Also published asDE844630C
Publication numberUS 2558752 A, US 2558752A, US-A-2558752, US2558752 A, US2558752A
InventorsHolm Sven
Original AssigneeAir Preheater
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Regenerative heat exchanger
US 2558752 A
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Description  (OCR text may contain errors)

July 3, 1951 s. HOLM REGENERATIVE HEAT EXCHANGER 2 Sheets-Sheet 1 Filed July 9, 1948 SVEN HOLM INVENTOR FILM CONDUCTANCE July 3, 1951 s. HOLM 2,558,752

REGENERATIVE HEAT EXCHANGER Filed July 9, 1948 2 Sheets Sheet 2 PLHTES WITH INTEGRHL T08 FINS cau vew 770mm SPO an it coRRuoare-n PLATES S VE/V H0 M INVENTOR.

FRICTION POWER x DENSITY Z 2 j:r+ -Rrr Les 1 BY FvcL l-M Fig. 5.

Patented July 3, 1951 REGENERATIVE HEAT EXCHAN GER Sven Holm, Wellsville, N. Y., asslgnor to The Air Preheater Corporation, New York, N. Y.

Application July 9, 1948, Serial No. 37,752

4 Claims. (Cl. 257-6) The present invention relates to heat exchange apparatus and particularly to improvements n the heat absorbing surface of regenerative air preheaters.

A conventional regenerative air preheater of the Ljungstrom type includes a rotor carrying heat absorbing surface in the form of metallic plates that are first positioned in a gas passage to absorb heat and then upon turning of the rotor become disposed in the air passage to impart heat to air flowing therethrough. Such heat absorbing surface requires periodical cleaning to remove ash and other impurities deposited thereon by the gases and for this purpose it is customary to use cleaning nozzles that provide streams of compressed air or high pressure steam jets. It has been noted that the elements, particularly at the hot end of the preheater, sometimes rupture and break and it has been discovered that this breakage is due to the force imposed by the high pressure streams of cleaning fluid, particularly when utilizing steam which, upon entering the channels between the plates expands and creates a separating force on the plates thereb causing stresses which, in combination with shock and vibrations imparted to the plates, results in their rupture. An object of the present invention is to overcome this disadvantageous condition and the manner in which it is carried out Will be best understood upon consideration of the following detailed description when read in conjunction with the accompanying drawings in which:

Figure 1 is a plan view of a regenerative type air preheator equipped with washing nozzles.

Figure 2 is a fragmentary perspective view on an enlarged scale of part of the heater shown in Fig. 1 illustrating the novel heat absorbing surface embodying the present invention;

Figure 3 is a further enlarged fragmentary perspective view showing an alternative form for the heat exchange plates;

Figure 4 illustrates a monolithic heat exchange mass made up of heat exchange plates embodying the invention; and

Figure 5 is a diagram illustrating the heat exchange efliciency of the present plates as compared with conventional corrugated or undulated plates.

In the drawings, the numeral l0 designates the cylindricalshell of a rotor which is divided into sector shaped compartments II by radial partitions [2 connecting it with the rotor post l3. A motor and reduction gearing l4 connected to the rotor post turn the rotor slowly about its axis. The rotor compartments I I which may be further subdivided by a circumferential partition l5 contain regenerative heat transfer material in the form of metallic plates l6 which are spaced apart to form narrow passages parallel to the rotor axis. The plates l6 first absorb heat from hot gases flowing through the gas passage ll of the preheater and, as the rotor turns slowly about its axis, the heated plates 16 are moved into the stream of air flowing through the air passage ll to-which a forced draft fan (not shown) is connected. After passing over the plates l6 and absorbing heat therefrom the stream of air is conveyed to a boiler furnace or other place of use. A soot blower 20 has one or more rotary nozzles 24 disposed above the rotor so that jets of cleaning fluid under pressure may be directed into the passages between the plates for cleaning them as disclosed in the patent to Waitkus, 2,355,021, issued August 1, 1944.

In accordance with the present invention the heat exchange plates l6 are each formed, preferably over their entire area, with a plurality of relatively small perforations 30 shown as arranged in parallel rows. These perforations are illustrated as of rectangular shape and are created by cutting through the plate material along opposite edges of the apertures and bending up the plate material so that the rectangular tab portions 3| which formerl filled the apertured portions of the plates project at right angles from the plate surface. In the form shown in Figs. 2 and 3 two tabs 3|, 32 are created adjacent each aperture by slitting the mid-portion of the material from the aperture parallel to its side edges 34 as well as along its top and bottom edges 35, 36 thus dividing the tab into two parts hinged at opposite edges of the perforation. In Fig. 4 the tabs 3| are connected to the body of the plate It only at one side edge 34 of the aperture 30.

When mounted in the compartments of a rotary regenerative air preheater, either throughout the height of the latter or, alternatively, only in the hot end section heat exchange plates embodying the present invention provide a heat absorbing surface which eliminates the stresses and shocks imposed on the plate material due to entry of high pressure steam into the passages between the plates as has been experienced heretofore because with the present plates the apertures 33 permit the steam to expand and pass through the plates instead of becoming confined and exerting a pressure on the surface of plates which strains them, subjects them to shock and vibration and eventually disrupts them. In addition to this, the tabs 3|, 32 extending from the sur- 3 faces of the. plates it serve useful functions, one being to act as spacers for holding the plates in properly spaced relation to form passages through the heat exchange mass without the use of specially provided separators.

A further important function performed by the tabs 3|. 32 is to increase the effectiveness of the heat exchange surfaces because they act as integral extensions of the plates and a greater efficiency is obtainable. than when the heat is exchanged merely by contact with the streams of fluid flowing in film contact with the plate surface itself. The fact that the planar surface is interrupted at intervals by the tabs maintains a thin boundary layer that does not impede heat transfer. In this form also more of the plate material is actually disposed in the stream of gases and by staggering the tabs projecting from the apertures as illustrated in Fig. 3 further efficiency is attainable because the streams of gases and air are continually interrupted and divided by contact with the staggered tabs in their passage through the rotor. The fin-like tabs 3|, 32 which are in alinement form interrupted strip fins in two planes extending both in the direction of gas flow and transversely thereof, considering the wider faces of the tabs as cross-sectional portions of transverse fins. To function effectively as heat transfer surface the tabs should extend in closely spaced relation parallel to the direction of flow to. provide free lanes therebetween for the flow of gases without producing an undesirable draft loss or causing useless turbulence since this is not desired.

A comparison of the heat exchange efficiency of the present plates as compared with conventional Ljungstrom undulated plates is shown in Fig. 5 wherein film conductance is plotted against the product of friction power by the gas -density? squared. A concomitant advantage of this marked increase in heat transfer efficiency is that for a given recovery the amount of plate surface of like gauge material required in a preheater is reduced by approximately fifty per cent (50%). This permits the height of the preheater rotor to be reduced (about or its diameter correspondingly lessened and itsvolume decreased (to about 68%). At the cold end greater heat transfer may be attained by increasing the gauge of the plates while at the same time reducing their height. In addition to the saving in cost of plate material the weight of the preheater assembly is less with the result that a saving may also be effected in the structural steel supporting the unit. Less power also is required to operate the unit for driving it.

ascents cause a single block would be quickly deposited in each rotor section instead of -a large number of separate plates that require individual han- By stacking in contact with each other a number of plates l6 sufficient to fill one of the rotor compartments II or a sub-division thereof and then bonding them together, as by dipping in a brazing bath etc. a unitary heatexchange mass may be produced. This mass would be a unitary structure having a series of passages for gas flow parallel to the axis of the rotor which passages would be created by the spacing function of the tabs 3|, 32 and would be cross-connected by the plate perforations 30. In addition to its heat exchange qualities such masses would have the considerable advantage of greatly reducing the time of erection of a preheater bedling or special bundling.

Figure 4 also illustrates a fin construction in which the metallic tab 3| is trapezoidal in form, having tapered and divergent side edges 0 which made the distal end a wider than the hinged end b. This facilitates the stacking of a number of plates since the distal ends a being wider than the major part of the perforation prevent the tabs or fins 3| from slipping inadvertently through perforations in adjacent plates.

Another advantage is presented by this form of surface. In a counterflow heat exchanger, heat always flows from the hot end of the heating surface to the cold end of the surface. This condition lowers the effectiveness of the heat exchanger and the amount of heat flowing this way is a function of the length of the path of flow. It is therefore evident that with the present surface the heat flow path for a given depth of surface is longer. Due to the surface being interrupted by the perforations the possible path for flow of conducted heat is not direct but because of the perforations becomes tortuous and therefore considerably longer. The cross-sectional area for conducted heat flow is also reduced. Hence less heat flows uselessly along plates and the heat flow area is also restricted between the perforations.

What I 'claim is:

1. In a regenerative air preheater or the like having a cylindrical rotor divided by partitions into compartments that carry heat transfer material; a pressurized fluid jet apparatus disposed and arranged for cleaning said material; heat transfer plates disposed in said compartments parallel to the direction of fluid flow and closely spaced to form narrow fluid passages therebetween axially of the rotor, each plate being formed over substantially its entire area with a myriad of perforations uniformly distributed over the plate area in parallel rows permitting passage of fluid between said passages laterally through the plates for minimizing pressure effects on the plates caused by the cleaning jets.

2. In a regenerative air preheater or the like having a cylindrical rotor divided by partitions into compartments that carry heat transfer material; heat transfer plates serving as primary surface disposed in said compartments parallel to the direction of fluid flow and closely spaced to form narrow fluid passages, each plate being formed over substantially its entire area with a myraid of closely spaced perforations arranged in parallel rows and the plate material from the perforations remaining to constitute tabs attached to the body of the plate along at least one edge of each aperture and being bent to extend therefrom into the passages provided between the plates for fluid flow and lie in planes parallel to the direction of fluid flow.

3. A monolithic primary heat exchange mass comprising a plurality of metallic plates each formed over substantially its entire area with relatively small apertures uniformly distributed in parallel rows the material from which remains as tabs attached at one edge of the apertures to the plates and is bent out perpendicular to the surface thereof to contact an adjacent plate for spacing adjacent plates to form fluid passages therebetween, the plates being bonded, as by brazing, into a unitary mass.

4. In a regenerative air preheater or the like axially of the rotor between said plates for sepahaving a cylindrical rotor divided by partitions REFERENCES orrEn cmpartments that carry heat transfer The following references are of record in the terlal; heat transfer plates disposed in said compartments parallel to the direction of fluid flow me of this patent' and closely spaced to form narrow fluid passages 5 UNITED STATES PAW therebetween axially of the rotor, each plate be- Number Name Date ing formed over substantially its entire area with 1,873;052 Seward Aug. 23, 1932 a myraid of perforations uniformly distributed in 1,983,549 Krackowizer Dec. 11, 1934 parallel rows over the plate area permitting pas- 2,347,857 Waitkus May 2, 1944 sage of, fluid between said passages laterally 5 2,428,145 Cook Sept. 30, 1947 through the plates; and spacer means extending FOREIGN PATENTS rating the latter to form said fluid passages. Number Country Date SVE'N HOLM. 715,051 France Nov. 25, 1931

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US715051 *Jun 11, 1901Dec 2, 1902Emile Marie Albert GimmigParcel-carrier.
US1873052 *Nov 19, 1928Aug 23, 1932Bush Mfg CompanyRadiator
US1983549 *May 10, 1933Dec 11, 1934Refrigeration Appliances IncRadiator fin
US2347857 *Oct 15, 1941May 2, 1944Air PreheaterTemperature zoned air preheater
US2428145 *Sep 11, 1944Sep 30, 1947Pacific Metals Company LtdHeat transfer fin
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US2680009 *Feb 25, 1953Jun 1, 1954Rca CorpCooling unit
US2703700 *Nov 22, 1950Mar 8, 1955Modine Mfg CoHeat interchanger
US2988336 *Apr 18, 1958Jun 13, 1961Air PreheaterHeat exchanger
US3211633 *May 28, 1962Oct 12, 1965Westinghouse Electric CorpFalling film distillation unit apparatus
US4405011 *Sep 28, 1981Sep 20, 1983The Air Preheater Company, Inc.Element basket
US5918368 *Aug 27, 1997Jul 6, 1999Solar Turbines, Inc.Method for making a recuperator cell
US5924478 *May 8, 1997Jul 20, 1999Caterpillar Inc.For a mobile work machine
US6158121 *Jan 14, 1999Dec 12, 2000Solar Turbines IncorporatedMethod and apparatus for making a recuperator cell
US6450245Oct 24, 2001Sep 17, 2002Alstom (Switzerland) Ltd.Air preheater heat transfer elements
EP1623175A2 *Apr 15, 2004Feb 8, 2006Sunpower, Inc.Involute foil regenerator
Classifications
U.S. Classification165/5, 29/890.34, 165/10, 165/DIG.110
International ClassificationF28D19/04, F28G9/00
Cooperative ClassificationF28D19/044, Y10S165/011, F28D19/042, F28G9/005, F28D19/04
European ClassificationF28G9/00B, F28D19/04, F28D19/04B2, F28D19/04B2B